EP2365116B1 - Rotationsschaftmaschine und mit einer solchen Schaftmaschine ausgestattete Webmaschine - Google Patents

Rotationsschaftmaschine und mit einer solchen Schaftmaschine ausgestattete Webmaschine Download PDF

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Publication number
EP2365116B1
EP2365116B1 EP11157534.6A EP11157534A EP2365116B1 EP 2365116 B1 EP2365116 B1 EP 2365116B1 EP 11157534 A EP11157534 A EP 11157534A EP 2365116 B1 EP2365116 B1 EP 2365116B1
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EP
European Patent Office
Prior art keywords
driving element
dobby
driving
latch
engaged
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EP11157534.6A
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English (en)
French (fr)
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EP2365116A1 (de
Inventor
Robert Nocenti
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Staubli Faverges SCA
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Staubli Faverges SCA
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Publication of EP2365116A1 publication Critical patent/EP2365116A1/de
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    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C1/00—Dobbies
    • D—TEXTILES; PAPER
    • D10—INDEXING SCHEME ASSOCIATED WITH SUBLASSES OF SECTION D, RELATING TO TEXTILES
    • D10B—INDEXING SCHEME ASSOCIATED WITH SUBLASSES OF SECTION D, RELATING TO TEXTILES
    • D10B2331/00—Fibres made from polymers obtained otherwise than by reactions only involving carbon-to-carbon unsaturated bonds, e.g. polycondensation products
    • D10B2331/02—Fibres made from polymers obtained otherwise than by reactions only involving carbon-to-carbon unsaturated bonds, e.g. polycondensation products polyamides
    • D10B2331/021—Fibres made from polymers obtained otherwise than by reactions only involving carbon-to-carbon unsaturated bonds, e.g. polycondensation products polyamides aromatic polyamides, e.g. aramides

Definitions

  • the invention relates to a rotating dobby for the control of heald frames mounted on a loom, and to a loom equipped with such a dobby.
  • each disk has a very low axial thickness which reduces their interaction zone with a rocker which must also be provided in the thickness of the disk.
  • the motion transmission efforts to a heald frame pass through the contact interface between one of these disks and the rocker. This interface being narrow, the contact pressures are very high, which induces premature wear of the dobby and the breakage of certain parts.
  • the drive mechanism of the oscillating disk must be built in the division, which decreases the volume available for the aforementioned disks.
  • the invention intends to remedy more particularly by proposing a new rotary dobby that makes it possible to give a movement to the frames of the loom, including when these must not be moved from an upper position to a lower one. lower position or vice versa, while being more reliable and simpler to manufacture than those of the state of the art.
  • the invention relates to a rotary dobby for a loom, this dobby comprising, for each of its blades, an oscillating piece coupled to a heddle frame and associated with an actuating element mounted loosely on a central shaft , a first driving element of the actuating element, integral in rotation with the central shaft, a second driving element of the actuating element and at least one latch mounted on the operating element and capable of securing in rotation this actuating element with either the first driving element or with the second driving element, while one of the two driving elements is driven in a rotational movement in a only in one direction and that the other drive element is reciprocated.
  • This dobby is characterized in that the second driving element is arranged around the first driving element and in that the latch is disposed in a space defined radially between the first driving element and the second driving element.
  • the first and second drive elements can be arranged in the same width of the division, which allows them to be given a thickness, taken parallel to the axis of rotation of the central shaft, greater than that of the disks of the known dobby of EP-A-1,516,947 . It is thus possible to increase the contact surfaces between these drive elements and the lock or locks, this or these latches not increasing the axial size of the force transmission mechanism since they are located radially between the first driving element and the second driving element.
  • the invention relates to a loom equipped with a dobby as mentioned above.
  • the dobby R represented at Figures 1 to 5 comprises a central shaft 1 driven, in normal operation of the dobby, a continuous rotation movement in one direction, at a constant speed, about its longitudinal axis X 1 , this movement being represented by the arrow F 1 in the figures .
  • This shaft 1 receives a series of bearings 2, in number equal to that of the heald frames 3 of the loom M to which belongs the dobby R.
  • On each bearing 2 is mounted fou an eccentric 4 on which is mounted crazy the opening of an oscillating rod 5 around a second bearing 2 '.
  • the free end 51 of the rod 5 is coupled to a pivoting arm 6 by means of a connecting plate 7.
  • the pivoting arm 6 is hinged about an axis X 6 parallel to the axis X 1 and defined by a shaft 61 fixed relative to the frame of the dobby R.
  • the movement of the pivoting arm 6 ensures, thanks to a connection rods 62, the vertical displacement of a heald frame 3, which is represented very schematically for the clarity of the drawing, according to a vertical oscillations movement represented by the double arrow F 2 at the figure 1 .
  • Each dobby blade R comprises a drive disc 8 whose central opening is substantially circular and provided with two teeth 81 engaged in longitudinal grooves of corresponding shape 1a formed at the periphery of the shaft 1.
  • the disc 8 being secured in rotation of the shaft 1, it has a rotary motion at a constant speed represented by the arrow F 8.
  • the outer peripheral edge 82 of the disk 8 is provided with four notches 83a, 83b, 83c and 83d which are formed in the thickness or the edge of the disk 8.
  • Each notch 83a to 83d has a generally triangular shape.
  • Two latches 10 and 11 are respectively articulated around two shafts 12a and 12b fixed on the eccentric 4 and each defining a geometric axis X 10 , X 11 of rotation a lock 10 or 11 with respect to the eccentric 4.
  • the axes X 10 and X 11 are parallel to the axis X 1.
  • a drive ring 13 is disposed around each drive disk 8 at the same level along the axis X 1 .
  • each drive ring 13 radially surrounds a drive disk 8 extending around its outer radial edge 82 and each blade of the dobby comprises both a drive disk 8 and a crown Training 13.
  • the ring 13 and the disk 8 may have the same axial thickness, or comparable axial thicknesses, substantially equal to the difference between the division, of the order of 12 mm, and the thickness of the eccentric 4, with the clearance .
  • each ring 13 is provided with four notches 133a, 133b, 133c and 133d which are intended to cooperate selectively with the bolts 10 and 11 and are formed in the thickness or the edge of the ring 13.
  • Each notch 133a to 133d has a generally triangular shape.
  • the notches 83a and 83c are diametrically opposed, as are the notches 83b and 83d, the notches 133a and 133c and the notches 133b and 133d.
  • the various drive rings 13, which are flat and extend parallel to each other along the shaft 1, are separated by spacers 14 and assembled by tie rods 14a, so that they constitute a rigid assembly or cradle which can be rotated alternately about the axis X 1 by a suitable mechanism, mechanical or electrical type which is disposed outside the area where the blades are formed, for example in the vicinity of one end of the 1.
  • Each ring 13 thus has an alternating rotation movement about the axis X 1 , this movement being represented by the arrows F 13 , in the same direction as the arrow F 8 , and F '13 , in a direction opposite to the arrow F 8 , and having an angular amplitude of 60 °.
  • the locks 10 and 11 are arranged in an annular space E defined between the respective peripheral edges 82 and 132 of the drive disk 8 and the drive ring 13.
  • This annular space opens at the two axial faces of the disk 8 and of the two axial faces of the crown 13.
  • the space E is identified as a shaded area at the figure 2 only.
  • the latch 10 comprises two lugs 101 and 102 which extend from an annular body 103 mounted around the shaft 12a.
  • the end 104 of the tab 101 is intended to be selectively engaged in one of the openings 83a and 83c, while the end 105 of the tab 102 is intended to be selectively engaged in one of the notches 133a and 133c.
  • the latch 10 also comprises a control lug 106 intended to cooperate with one of two identical rockers 15 and 16 hinged to the drive ring 13.
  • the constituent parts of the latch 11 bear the same references as those of the latch 10 increased by 10.
  • the latch 11 thus comprises two lugs 111 and 112 which extend from a body 113 and end with ends 114 and 115 intended to be respectively selectively engaged in the notches 83b and 83d, 133b and 133d, then a control lug 116 allows it to interact with one of the rockers 15 and 16.
  • the bolts 10 and 11 are identical except at the level of the control lugs 106 and 116 which are provided to be superimposed in the thickness axial of the space E.
  • Each of the latches 10 and 11 is designed to be engaged with either the drive disk 8 or with the drive ring 13, the two latches 10 and 11 being simultaneously engaged with the same drive element.
  • the rocker 15 is articulated on a shaft 17a passing right through the ring 13.
  • the rocker 15 is formed by the assembly of two plates 15a and 15b interconnected by two spacers 15c and 15d.
  • the spacer 15c is located radially outside the ring 13, that is to say connects the plates 15a and 15b beyond the peripheral outer radial edge 137 of the ring 13 with respect to the X axis. 1 .
  • the spacer 15d connects the plates 15a and 15b to the inside of the ring 13, that is to say in the vicinity of its internal radial edge 132.
  • a notch 135 is provided in the internal radial edge 132 to accommodate spacer 15d.
  • the plates 15a and 15b are each provided with a hook 15e, these hooks being folded towards each other so as to define together a bridge 15f which extends between the plates 15a and 15b.
  • the rocker 15 is mounted as a yoke around a portion of the ring 13, the plates 15a and 15b being disposed on the two opposite axial faces of the drive ring 13. This allows each of the spacers 15c and 15d to have a thickness axial e 15 substantially equal to that of the ring 13.
  • the rocker 16 is identical to the rocker 15 and articulated on the drive ring 13 around a second shaft 17b.
  • 16c and 16d are the spacers of the rocker 16 which are respectively similar to the spacers 15c and 15d.
  • the tilters 15 and 16 are mounted on the ring 13 so that the spacers 15c and 16c, on the one hand, 15d and 16d, on the other hand, are diametrically opposed.
  • Two stops 18 and 19 are mounted on the eccentric 4 on the same side as the shafts 12a and 12b.
  • two return levers 20 and 21 are respectively mounted on the eccentric 4, on the same side as the shafts 12a and 12b and housed in the space E, respectively close to the bolts 10 and 11.
  • the levers 20 and 21 are respectively articulated around two shafts 22a and 22b parallel to the shafts 12a and 12b.
  • X 20 and X 21 respectively denote the axes of articulation of the levers 20 and 21 with respect to the eccentric 4.
  • the lever 20 comprises a first arm 201 resting against the lug 101 of the latch 10, on the side of this lug opposite the drive disk 8.
  • the lever 20 also comprises a second arm 202 subjected to an elastic force E 23 exerted by a spring 23 bearing against the stop 18.
  • the force E 23 is transmitted to the latch 10 in the form of a force E 20 exerted by the arm 201 of the lever 20, the force E 20 having the effect of pressing the arm 201 against the external radial edge 82 of the drive disk 8.
  • a spring 24 bearing on the stop 19 exerts on the lever 21 an elastic force E 24 that the lever 21 transmits to the latch 11 in the form of a E 2 force , which plate the tab 111 of the latch 11 closest to the drive disc 8 against the outer radial edge 82 of the drive disc 8.
  • rocker 15 is subjected to the action of a spring 25 disposed in a housing 136 constituted by a hole formed through the drive ring 13.
  • the bridge 15f is also engaged in the housing 136 and is under a stress elastic E 25 exerted by the spring 25, this elastic force tending to press the spacer 15d against the bottom of the notch 135, that is to say to move this spacer 15d control tabs 106 and 116 locks 10 and 11.
  • the rocker 16 is also mounted on the drive ring 13 with the interposition of a spring 26 which exerts a force E 26 tending to press its inner spacer 16d in the bottom of the notch provided for this purpose on the internal radial edge 132 of the drive gear 13.
  • the dobby R also comprises two oscillating levers 30 and 31 each articulated around a shaft 32a or 32b which is fixed relative to the frame of the dobby.
  • X 30 and X 31 respectively denote the axes of articulation of the oscillating levers 30 and 31 which are defined by the shafts 32a and 32b.
  • the oscillating lever 30 is equipped with a roller 33 designed to roll on a portion 137a of the outer radial peripheral edge 137 of the drive ring 13, as well as on the spacer 15c of the rocker 15, depending on the weave.
  • the oscillating lever 31 is equipped with a roller 34 designed to roll on a portion 137b of the edge 137 and on the outer spacer 16c of the rocker 16, depending on the armor.
  • a selection device 35 which comprises an electromagnet 36 and a selection finger 37, is provided to come into selective engagement with the end 30a of the lever 30 opposite the roller 33 and the end 31a of the lever 31 opposite the roller 34.
  • the selection device 35 makes it possible to hold one or the other of the levers 30 and 31 in position and to hold the roller 33 or 34 of the lever 30 or 31 on which it acts away from the rocker 15 or 16 adjacent.
  • Unrepresented springs exert on the levers 30 and 31 elastic forces E 30 , E 31 which tend to rotate these oscillating levers about the axes X 30 and X 31 in a direction such that the rollers 33 and 34 are moved in the direction of the axis X 1 and that the ends 30a and 31a are remote from this axis.
  • the drive disc 8 constitutes a first element for rotating the eccentric 4, with a rotation movement F 8 in one direction, at a constant speed.
  • the driving ring 13 constitutes a second drive element of the eccentric 4, with an alternating rotational movement F 13 and F '13 .
  • the rotation of the elements 4, 8 and 13 takes place around the axis X 1 .
  • each of the frames 3 is defined for each pick, that is to say each insertion of a weft yarn.
  • a frame can be made to change from an upper position P SUP to a lower position P INF through an intermediate or median position P MED , or vice versa, which is considered a movement basic, or main movement.
  • the frame maintains a higher position, with a low amplitude movement, it performs a secondary movement between the upper position P SUP and a position P ' SUP located above the median position P MED and close to the upper position.
  • the frame When the frame maintains a lower position, it performs a secondary movement between the lower position P INF and a position P ' INF located below the median position P MED and close to the lower position.
  • the difference in height between the positions P INF and P ' INF is less than half the difference in height between the positions P SUP and P INF.
  • the secondary movement takes place over more than 360 ° of craft angle.
  • the basic movement of a heald frame 3 is a portion of sinusoidal motion with a period equal to 720 ° of working angle, between the position P INF and the position P su p or vice versa.
  • This movement is obtained by the conversion of a driving movement of the eccentric 4 by the drive disc 8 which is driven by a uniform rotational movement in one direction, with a period equal to 720 ° of work angle .
  • This is represented by the portion of curve in solid line extending between 720 ° and 1800 ° of angle of the trade ⁇ to the figure 5 and which represents the position P of a frame according to the angle of the craft, during its movements according to the arrow F 2 -
  • N 1 to N 8 are shown.
  • a secondary movement of the heald frame 3 can be obtained when the eccentric 4 is driven by the ring 13, with an alternating rotational movement, which corresponds to the curve portion shown in solid lines between the angles of occupation 360 and 720 to the figure 5 .
  • This secondary movement also corresponds to the curve portion shown in solid line between the angles 1800 ° and 2160 ° in this figure.
  • the portion of the curve between the angles 360 ° and 720 ° corresponds to a secondary movement occurring near the upper position P SUP of a frame that the frame reaches at the pick N 2 and retains the pick N 3 , then that the portion of the curve between the angles of occupation 1800 and 2160 corresponds to the secondary movement occurring near the lower position P INF than the frame reached at the pick N 6 and kept at the pick N 7 .
  • the secondary movement between the 360 ° and 720 ° occupation angles takes place between the positions P SUP and P ' SUP , with an amplitude equal to the difference in height of these positions.
  • the secondary movement between the angles 1800 ° and 2160 ° takes place between the positions P INF and P ' INF , with an amplitude equal to the difference in height between these positions.
  • the assembly or cradle constituted by the various driving rings 13 secured to each other is controlled so that the secondary movement of a frame 3 driven by one of these rings 13 is a portion of sinusoidal frequency movement four times as much. high than the base movement and amplitude equal to 1/16 th of the base movement amplitude, which corresponds to an oscillation of the set of crowns 13 of amplitude equal to 60 °.
  • the angular amplitude of the movement of the rings 13 is between 30 ° and 120 °, preferably between 45 ° and 90 °, the value of 60 ° proving very advantageous.
  • the movement of the ring 13 has a reduced angular amplitude with respect to the complete rotational movement of the disk 8. This has the consequence that the amplitude of movement according to the arrow F 2 of the frame 3 driven by the ring 13 is reduced with respect to the amplitude of this movement when the frame is driven by the disk 8.
  • the frame 3 when it is driven by the ring 13, the frame 3 remains at near its upper end position, that is to say its upper position P SUP , or in the vicinity of its lower end position P INF , that is to say, its lower position.
  • the difference in height between P SUP and P ' SUP or between P INF and P' INF is equal to 1/16 of the difference in height between P SUP and P INF
  • the frequency of the secondary movement of the frames 3 may be another multiple of four times the frequency of the basic movement of the frames 3, for example equal to eight times or twelve times this frequency.
  • the figure 5 shows in dotted lines the instantaneous velocity curve V of an animated frame of the movement represented by the solid line curve and in axial lines the instantaneous acceleration curve A of this frame.
  • the movement represented by the position curve P is a non-stop movement, the acceleration of a frame being non-zero when its speed is zero.
  • the elements 8 and 13 have the same instantaneous angular velocities and the same instantaneous angular accelerations with respect to the axis X 1 .
  • the driving elements 8 and 13 are driven in a rotation movement in the same direction, thanks to the secondary frequency movement 4 times greater than that of the base movement. There is therefore no discontinuity of movement, speed and acceleration of the frame 3 at the transfer points, even if there has been switching.
  • the rollers 33 and 34 roll against the portions 137a and 137b of the outer edge 137, or a portion of these portions, which makes it possible to obtain a leveling of the levers 30 and 31 by rotating them against the efforts E 30 and E 31 .
  • the selection device 35 can retain the end 30a or 31a of one of them depending on the power supply of the electromagnet 36 which depends on the armor, to cause or not switching locks 10 and 11.
  • the levers 30 and 31 are leveled and the selection device 35 blocks the lever 31 without interacting with the lever 30.
  • This action of the rocker 15 on the bolts 10 and 11 has the effect of pivoting respectively about the axes X 10 and X 11 in a direction of release of the ends 104 and 114 relative to the notches 83c and 83b, while engaging the ends 105 and 115 respectively in the notches 133c and 133b.
  • the action of the lever 30 on the rocker 15 makes it possible to separate the eccentric 4 with respect to the drive disc 8 and to secure it to the drive ring 13, so that the frame 3 is then animated secondary movement.
  • the action of the rocker 15 on the bolts 10 and 11 takes place against the forces E 23 and E 24 .
  • the latches 10 and 11 work in compression to transmit the movement of one of the driving elements 8 or 13 to the eccentric 4, which ensures a duration
  • the fact that the rollers 33 and 34 roll on the portions 137a and 137b of the outer edge 137 allows this edge to provide a leveling function, as envisaged in FIG. EP-A-1,382,725 , so that the selection device 35 is dimensioned only to withstand the forces E 30 and E 31 , without having to positively move the levers 30 and 31.
  • the two latches 10 and 11 In operation, depending on whether the frame 3 accelerates or decelerates, the two latches 10 and 11 alternately join the eccentric 4 with the drive element, whether this element is the disk 8 or the ring 13. In a phase of movement of the 3, a single latch 10 or 11 secures the eccentric 4 with one of the driving elements 8 or 13, while in another phase of movement, it is the other latch 11 or 10 which provides this function of solidarity.
  • the driving elements 8 and 13 have the same axial thickness. Alternatively, they may have different thicknesses.
  • the rockers 15 and 16 may not act directly on the control tabs 106 and 116 of the locks 10 and 11 but on a slide movable in translation in a radial direction relative to the axis X 1 and received in a housing of the eccentric 4, the ends of the tabs 106 and 116 being articulated on the slide.
  • the lock 10 is provided with a head 108 having two teeth 108a and 108b which can be selectively engaged in one of the two notches 83a and equivalent of the drive disk 8 and in one of the two notches 133a and equivalent of the drive ring 13.
  • the notches 83a, 133a and equivalent are respectively formed on the outer radial edge 82 of the disk 8 and on the inner radial edge 132 of the ring 13.
  • the latch 10 is disposed radially in a space E which extends between the disk 8 and the ring 13 and it allows to mechanically couple the eccentric 4 is to disc 8 to crown 13.
  • a stop 18, a lever 20 and a spring 23 operate as those of the first embodiment.
  • the lock 10 is unique and comprises a piston 109 loaded elastically by two springs 23 and 24 which each exert a force centrifugal E 23 or E 24 tending to engage an outer radial portion 109a of the piston 109 in one of two notches 133a and equivalent formed on the inner radial edge 132 of the drive ring 133.
  • the drive is provided with two notches 83a and an equivalent selective receiving of an inner radial portion 109b of the piston 109.
  • a slider 15 and its equivalent, not shown and diametrically opposed with respect to the slider 15, are arranged in the ring 13 with a possibility of translation in a radial direction and allow to exercise selectively on the piston 109 a force of engagement of the portion 109b in the notch 83a or the equivalent notch.
  • the latch 10 is clutched on the drive ring 13 and, when it is desired to lock the latch 10 in rotation with the disk 8, it suffices to leave the roller 33 or equivalent of the one of the oscillating levers 30 and equivalent acting on the slider 15 or equivalent near which the lock 10 is located.
  • the latch 10 is disposed in a space E which extends radially between the outer and inner edges 82 and 132 of the drive elements 8 and 13 and the drive ring 13 is arranged radially around the drive disc 8 .
  • the oscillating levers 30 and 31 can act directly on the locks mounted on the eccentric.
  • the invention is described above in the case where the shaft 1 and the discs 8 are driven in a rotary motion in one direction, while the rings 13 are moved in a reciprocating motion.
  • the invention also relates to the opposite case where the central shaft and the disks 8 are driven by an alternating rotational movement, whereas the set of rings 13 is driven by a continuous rotational movement in one direction only. preferably at constant speed.
  • a heald frame when a heald frame is driven from a ring 13, the amplitude of its movement of vertical oscillations is reduced with respect to its amplitude when it is driven by a disk 8 and the switching of the locks 10 and the equivalent, a securing position with the disk 8 to a position of attachment to the ring 13, or conversely, occurs when the frame is in the vicinity of its position higher or near its lower position.

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  • Textile Engineering (AREA)
  • Looms (AREA)

Claims (14)

  1. Rotationsschaftmaschine (R) für eine Webmaschine (M), wobei diese Schaftmaschine für jedes seiner Schäfte aufweist:
    - ein schwingendes Teil (5), das an einen Schaftrahmen (3) angekoppelt ist und einem Betätigungselement (4) zugeordnet ist, das freidrehend an einer Mittelwelle (1) befestigt ist,
    - ein erstes Antriebselement (8) des Betätigungselements, das drehfest mit der Mittelwelle verbunden ist,
    - ein zweites Antriebselement (13) des Betätigungselements und
    - mindestens einen Riegel (10, 11), der an dem Betätigungselement befestigt ist und geeignet ist, dieses Betätigungselement sei es mit dem ersten Antriebselement (8), sei es mit dem zweiten Antriebselement (13) drehfest zu verbinden,
    wobei eines der zwei Antriebselemente zu einer Bewegung in einer einzigen Richtung angeregt wird, während das andere Antriebselement zu einer alternierenden Drehbewegung angeregt wird,
    dadurch gekennzeichnet, dass das zweite Antriebselement (13) um das erste Antriebselement (8) herum angeordnet ist, und dass der Riegel (10, 11) in einem Raum (E) angeordnet ist, der radial zwischen dem ersten Antriebselement und dem zweiten Antriebselement begrenzt ist.
  2. Schaftmaschine nach Anspruch 1, dadurch gekennzeichnet, dass das erste Antriebselement (8) zu einer Drehbewegung (F8) in einer einzigen Richtung angeregt wird und dass das zweite Antriebselement (13) zu einer alternierenden Drehbewegung (F13, F'13) angeregt wird.
  3. Schaftmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass jeder Riegel (10, 11) mit einem ersten Teil (104, 114, 109b), das angepasst ist, selektiv in mindestens eine Ausnehmung (83a-83d) einzugreifen, die an einem äußeren radialen Rand (82) des ersten Antriebselements (8) angeordnet ist, und mit einem zweiten Teil (105, 115; 109a) versehen ist, das angepasst ist, selektiv in mindestens eine Ausnehmung (133a-133d) einzugreifen, die an einem inneren radialen Rand (132) des zweiten Antriebselements (13) angeordnet ist.
  4. Schaftmaschine nach Anspruch 3, dadurch gekennzeichnet, dass sie Mittel (23, 24) zur elastischen Vorspannung jedes Riegels (10, 11) in eine Position des Eingriffs seines ersten Teils (104, 114) oder seines zweiten Teils (109a) in eine Ausnehmung (83a-83d), die an dem äußeren radialen Rand (82) des ersten Antriebselements (8) oder in eine Ausnehmung (133a), die an dem inneren Rand radialen (132) des zweiten Antriebselements (13) angeordnet ist, umfasst.
  5. Schaftmaschine nach einem der Ansprüche 3 oder 4, dadurch gekennzeichnet, dass, wenn ein Riegel (10, 11) mit einem (8) des ersten und des zweiten Antriebselements in Eingriff ist, ein Teil (105, 115) dieses Riegels, das angepasst ist, selektiv in eine Ausnehmung (133a-133d) des anderen Antriebselements (13) einzugreifen, in einer gleitenden Anlage gegen den benachbarten Rand (132) des anderen Antriebselements (13) liegt.
  6. Schaftmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass zwei Riegel (10, 11) in dem Raum (E) angeordnet sind, der radial zwischen dem ersten Antriebselement (8) und dem zweiten Antriebselement (13) begrenzt ist, und dass der äußere radiale Rand (82) des ersten Antriebselements (8) und der innere radiale Rand (132) des zweiten Antriebselements (13) jeweils mit vier Ausnehmungen (83a-83d, 133a-133d) zur Aufnahme eines Teils (104, 105, 114, 115) eines Riegels (10, 11) versehen sind.
  7. Schaftmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die zweiten Antriebselemente (13), die zu unterschiedlichen Schäften der Schaftmaschine (R) gehören, drehfest um die Achse (X1) der Mittelwelle (1) angeordnet sind und zusammen eine Wiege bilden, die ihrerseits zur Drehung (F13, F'13) um diese Achse angetrieben wird.
  8. Schaftmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie für jeden Schaft zwei Schwinghebel (30, 31), die geeignet sind, durch eine Auswahlvorrichtung (35) in Stellung gehalten zu werden, und mindestens ein Organ (15, 16) umfasst, das an dem zweiten Antriebselement (13) befestigt ist und geeignet ist, eine Kraft (E33, E15) eines der Schwinghebel auf einen Riegel (10, 11) zu übertragen.
  9. Schaftmaschine nach Anspruch 8, dadurch gekennzeichnet, dass jedes Organ zur Kraftübertragung ein Kippelement (15, 16) ist, das um eine in Bezug auf das zweite Antriebselement (13) feste Achse (17a, 17b) schwenkend (F15) befestigt ist.
  10. Schaftmaschine nach Anspruch 8, dadurch gekennzeichnet, dass jedes Organ zur Kraftübertragung ein translatorisch gemäß einer radialen Richtung beweglicher Schlitten (15) an dem zweiten Antriebselement (13) ist.
  11. Schaftmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie für jeden Schaft zwei Schwinghebel (30, 31) umfasst, die geeignet sind, durch eine Auswahlvorrichtung (35) in Stellung gehalten zu werden, und dass mindestens ein Bereich (137a, 137b) eines äußeren radialen Randes (137) des zweiten Antriebselements (13) geeignet ist, mit einem Schwinghebel (30, 31) zusammenzuarbeiten und diesen Hebel in eine Stellung zu bringen, in der er von der Auswahlvorrichtung zurückgehalten werden kann.
  12. Schaftmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass, wenn sie in einer Konfiguration (Fig. 2) ist, in der der Riegel (10, 11) zwischen einer ersten Stellung (Fig. 1) im Eingriff mit einem der Antriebselemente (8) und einer zweiten Stellung (Fig. 4) im Eingriff mit dem anderen Antriebselement (13) gekippt werden kann, die zwei Antriebselemente (8, 13) zu einer Drehbewegung (F8, F13) in derselben Richtung angeregt werden.
  13. Schaftmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass, wenn sie in einer Konfiguration (Fig. 2) ist, bei der der Riegel (10, 11) zwischen einer ersten Stellung (Fig. 1) im Eingriff mit einem der Antriebselemente (8) und einer zweiten Stellung (Fig. 4) im Eingriff mit dem anderen Antriebselement (13) gekippt werden kann, die zwei Antriebselemente (8, 13) dieselben Winkelgeschwindigkeiten (V) und dieselben momentanen Winkelbeschleunigungen (A) in Bezug auf die Drehachse (X1) der Mittelwelle (1) aufweisen.
  14. Webmaschine (M), ausgerüstet mit einer Rotationsschaftmaschine (R) nach einem der vorhergehenden Ansprüche.
EP11157534.6A 2010-03-12 2011-03-09 Rotationsschaftmaschine und mit einer solchen Schaftmaschine ausgestattete Webmaschine Active EP2365116B1 (de)

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FR1051794A FR2957366B1 (fr) 2010-03-12 2010-03-12 Ratiere rotative et metier a tisser equipe d'une telle ratiere

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CN110117859B (zh) * 2018-02-06 2021-08-17 郑川田 可形成双织口的多臂机
CN108588950A (zh) * 2018-04-03 2018-09-28 西安工程大学 一种三维间隔织机的多页综框开口机构

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH671782A5 (de) * 1987-01-05 1989-09-29 Ernst Kleiner
FR2662186B1 (fr) * 1990-05-18 1992-08-28 Staubli Sa Ets Procede pour le montage des elements d'actionnement des ratieres rotatives pour metiers a tisser, et ratieres obtenues.
FR2663347A1 (fr) 1990-06-15 1991-12-20 Staubli Trumpelt Gmbh Maschine Ratiere a foule fermee pour metiers a tisser.
JPH07166444A (ja) * 1993-12-15 1995-06-27 Murata Mach Ltd ロータリードビー
JPH101842A (ja) * 1996-06-14 1998-01-06 Murata Mach Ltd ロータリードビー
FR2757883B1 (fr) * 1996-12-31 1999-02-19 Staubli Sa Ets Ratiere rotative et metier a tisser equipe d'une telle ratiere
FR2757882B1 (fr) * 1996-12-31 1999-02-19 Staubli Sa Ets Ratiere rotative et metier a tisser equipe d'une telle ratiere
FR2842538B1 (fr) * 2002-07-16 2004-10-29 Staubli Sa Ets Ratiere rotative pour metier a tisser, et metier a tisser equipe d'une telle ratiere
ITMI20022151A1 (it) * 2002-10-10 2004-04-11 Fimtextile Spa Dispositivo per attuare la programmazione di ratiere rotative per macchine di tessitura comportante mezzi di comando a motore elettrico rotativo perfezionati
ITMI20022695A1 (it) * 2002-12-19 2004-06-20 Fimtextile Spa Dispositivo per attuare la programmazione di ratiere rotative in macchine di tessitura
DE10343377B3 (de) * 2003-09-17 2005-04-28 Groz Beckert Kg Schaftantrieb für Webmaschinenschäfte
FR2899244B1 (fr) * 2006-03-31 2008-06-13 Staubli Faverges Sca Ratiere rotative, metier a tisser equipe d'une telle ratiere et element d'entrainement pour une telle ratiere
FR2899602B1 (fr) * 2006-04-11 2008-05-23 Staubli Faverges Sca Ratiere rotative, metier a tisser comprenant une telle ratiere et procede de commande d'une telle ratiere

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FR2957366B1 (fr) 2012-04-13
CN102191605B (zh) 2014-08-20
FR2957366A1 (fr) 2011-09-16
EP2365116A1 (de) 2011-09-14

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